US20120279327A1 - Final drive mechanism and power take off for a transmission - Google Patents
Final drive mechanism and power take off for a transmission Download PDFInfo
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- US20120279327A1 US20120279327A1 US13/552,717 US201213552717A US2012279327A1 US 20120279327 A1 US20120279327 A1 US 20120279327A1 US 201213552717 A US201213552717 A US 201213552717A US 2012279327 A1 US2012279327 A1 US 2012279327A1
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- bearing
- drive mechanism
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0215—Details of oil circulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
Definitions
- This invention relates to an automatic transmission for a motor vehicle that includes planetary gearsets and clutches and brakes whose state of engagement and disengagement determines speed ratios produced by the transmission.
- the axial space available for the transmission is limited by the width of the engine compartment and the length of the engine.
- the trend to increase the number of ratios available generally increases the number of components required. For these reasons, it is desirable to position components concentrically in order to minimize axial length.
- the ability to position components concentrically is limited, however, by the need to connect particular components mutually and to the transmission case.
- the output element is desirable for the output element to be located near the center of the vehicle, which corresponds to the input end of the gear box.
- An output element located toward the outside of the vehicle may require additional support structure and add length on the transfer axis. With some kinematic arrangements, however, the need to connect certain elements to the transmission case requires that the output element be so located.
- Chain drive transaxle final drive systems with grounded ring planetary gear sets have unacceptable noise, vibration and harshness properties due to chain lash.
- Transfer shaft gearing systems limit overall gear ratio.
- a drive mechanism includes a transmission including a pinion centered at an axis, a differential mechanism centered at a second axis forward of the axis, driveably connected to the pinion through a gear wheel meshing with the pinion, and a power take-off mechanism centered at a third axis rearward of the axis, driveably connected to the pinion, including a clutch that alternately opens and closes a drive connection to the pinion.
- the drive mechanism satisfies a vehicle styling requirement that locates the front wheel axles, with respect to the lateral axis of the vehicle, forward of the engine and provides all-wheel drive (AWD) operation.
- the power-take off (PTU) is integrated into the front wheel drive transaxle.
- FIG. 1 is a cross sectional side view of a multiple speed automatic transaxle
- FIG. 2 is cross sectional side view of the transaxle showing the front and middle cylinder assemblies
- FIG. 3 is a side perspective view showing sleeves that are fitted on the front support and middle cylinder assembly, respectively;
- FIG. 4 is a view cross sectional side view of the transfer gears and shaft near the output of the transaxle;
- FIG. 5 is a cross sectional side view of a multiple speed automatic transaxle having an alternate final drive mechanism from that of FIG. 4 ;
- FIG. 6 is a cross sectional side view of a multiple speed automatic transaxle showing a power take-off mechanism and an alternate final drive;
- FIG. 7 is a schematic diagram showing the arrangement of the principal axes of the transmission, power take-off mechanism and final drive of FIG. 6 .
- FIG. 1 illustrates gearing, clutches, brakes, shafts, fluid passages, and other components of a multiple-speed automatic transaxle 10 arranged substantially concentrically about an axis 11 .
- a torque converter includes an impeller driven by an engine, a turbine hydrokinetically coupled to the impeller, and a stator between the impeller and turbine.
- a transmission input shaft 20 is secured by a spline connection 21 to the turbine.
- the stator is secured by a spline connection 22 to a front support 24 , which is secured against rotation to a transmission case 26 .
- a double pinion, speed reduction planetary gearset 28 includes a sun gear 30 , secured by a spline connection 31 to input shaft 20 ; a carrier 32 , secured by a spline connection 33 to the front support 24 ; a ring gear 34 , secured by a spline connection 35 to a front cylinder assembly 36 ; a first set of planet pinions 38 supported on carrier 32 and meshing with sun gear 30 ; and a second set of planet pinions 40 , supported on carrier 32 and meshing with ring gear 34 and the first pinions 38 .
- Ring gear 34 rotates in the same direction as input shaft 20 but at a reduced speed.
- Rear gearset 46 and middle gearset 48 are simple planetary gearsets.
- Gearset 46 includes a set of planet pinion 50 supported for rotation on carrier 52 and meshing with both sun gear 54 and ring gear 56 .
- Gearset 48 includes a set of planet pinions 58 supported for rotation on carrier 60 and meshing with both sun gear 62 and ring gear 64 .
- Sun gear 54 is splined to a shaft that is splined to a shell 66 , on which shaft sun gear 62 is formed, thereby securing the sun gears 54 , 62 mutually and to the shell 66 .
- Carrier 52 is fixed to a shell 68 .
- Carrier 60 and ring gear 56 are fixed to each other and to output pinion 70 through a shell 72 .
- Ring gear 64 is fixed to shell 74 .
- Front cylinder assembly 36 which is fixed to ring gear 34 , actuates clutches 76 , 80 .
- Plates for clutch 76 includes plates splined to front cylinder assembly 36 alternating with plates splined to shell 74 .
- piston 78 When hydraulic pressure is applied to piston 78 , the plates are forced together and torque is transmitted between ring gears 34 and 64 .
- ring gears 34 and 64 When the hydraulic pressure is released, ring gears 34 and 64 may rotate at different speeds with low parasitic drag.
- plates for clutch 80 include plates splined to front cylinder assembly 36 alternating with plates splined to shell 66 .
- hydraulic pressure is applied to piston 82 , torque is transmitted between ring gear 34 and sun gears 54 , 62 . Pressurized fluid is routed from a control body 84 , through front support 24 , into front cylinder assembly 36 between rotating seals.
- Middle cylinder assembly 86 which includes carrier 32 , actuates brake 88 .
- Plates for brake 88 include plates splined to carrier 32 alternating with plates splined to shell 66 .
- the brake holds sun gears 54 , 62 against rotation.
- Pressurized fluid is routed from the control body 84 , through front support 24 , between planet pinions 38 , 40 , into middle cylinder assembly 86 . Due to the location of clutch pack 88 , output element 70 is located in the more favorable position near the front of the gear box.
- Rear cylinder assembly 92 is secured by a spline connection 93 fixed to input shaft 20 .
- the plates of clutch 96 transmit torque between input shaft 20 and carrier 52 .
- piston 98 the plates of clutch 100 transmit torque between input shaft 20 and sun gears 54 , 62 .
- Pressurized fluid is routed from the control body 84 , into rear cylinder assembly 92 .
- brake 104 When hydraulic pressure is applied to piston 102 , brake 104 holds carrier 52 and shell 68 against rotation.
- a one-way brake 106 passively prevents carrier 52 and shell 68 from rotating in the negative direction, but allows them to rotate in the forward direction.
- One-way brake 106 may optionally be omitted and its function performed by actively controlling brake 104 .
- the D brake 104 is used only as a latching device not as a dynamic brake. To minimize parasitic viscous drag loss produced in brake 104 it is desired that excess oil not be present in the brake. Therefore, an oil dam formed by an oil seal 103 between the piston 94 of E clutch 96 and the inner race 107 of one-way brake 106 is provided to limit or prevent oil from entering the D brake 104 .
- the inner radial end of return spring 108 continually contacts the piston 102 that actuates brake 104 .
- the outer radial end of return spring 108 continually contacts a fixed structure, so that the spring flexes as the piston 102 moves in the cylinder of the D brake 104 . In this way, return spring 108 also participates in the oil dam by limiting or preventing radial flow of oil into the D brake 104 caused by centrifugal force.
- brake 88 and clutches 76 , 80 to be mutually concentric, located at an axial plane, and located radially outward from the planetary gearsets 28 , 46 , 48 such that they do not add to the axial length of the gearbox.
- clutches 96 , 100 and brake 104 are mutually concentric and located radially outward from the planetary gearing 28 , 46 , 48 .
- Clutches 76 , 80 , 96 , 100 and brakes 88 , 104 , 106 comprise the control elements.
- FIGS. 2A , 2 B illustrate, the front cylinder assembly 36 is supported for rotation on the fixed front support 24 and carrier 34 .
- the front cylinder assembly 36 is formed with clutch actuation fluid passages, each passage communicating with one of the cylinders 114 , 116 formed in the front cylinder assembly 36 .
- Cylinder 114 contains piston 78 ;
- cylinder 116 contains piston 82 .
- One of the fluid passages in front cylinder assembly 36 is represented in FIG. 2 by interconnected passage lengths 109 , 110 , 111 , 112 , through which cylinder 116 communicates with a source of clutch control hydraulic pressure.
- Another of the fluid passages in front cylinder assembly 36 which is similar to passage lengths 109 , 110 , 111 , 112 but spaced angularly about axis 11 from passage lengths 109 , 110 , 111 , 112 , communicates a source of clutch control hydraulic pressure to cylinder 114 .
- Passage lengths 109 are machined in the surface at the inside diameter of the front cylinder assembly 36 .
- the front cylinder assembly 36 is also formed with a balance volume supply passage, similar to, but spaced angularly about axis 11 from passage lengths 109 , 110 , 111 , 112 .
- the balance volume supply passage communicates with balance volumes 120 , 122 .
- the balance volume supply passage includes an axial passage length 124 , which communicates with a source of balance volume supply fluid and pressure, and a radial passage length 126 , through which fluid flows into the balance volumes 120 , 122 from passage 124 .
- Passage 124 may be a single drilled hole extending along a longitudinal axis and located between the two clutch balance areas of the A clutch and B clutch. Passage 124 carries fluid to cross drilled holes 126 , which communicate with the balance volumes 120 , 122 .
- Coiled compression springs 128 , 130 each located in a respective balance dam 120 , 122 , urge the respective piston 78 , 82 to the position shown in FIG. 2 .
- Ring gear 34 is secured to front cylinder assembly 36 by a spline connection 132 .
- Middle cylinder assembly 86 includes carrier 32 , which is grounded on the front support 24 .
- Carrier 32 includes first and second plates 134 , 135 and pinion shafts secured to the plates, one pinion shaft supporting pinions 38 , and the other pinion shaft supporting pinions 40 .
- Plate 135 is formed with a cylinder 140 containing a brake piston 90 .
- a source of brake actuating hydraulic pressure communicates with cylinder 140 through a series on interconnected passage lengths 142 , 143 and a horizontal passage length that extends axially from passage 143 , through a web of carrier 32 , between the sets of planet pinions 38 , 40 , to cylinder 140 .
- These brake feed passages are formed in carrier 32 .
- piston 90 forces the plates of brake 88 into mutual frictional contact, thereby holding sun gears 54 , 62 and shell 66 against rotation.
- a Belleville spring 146 returns piston 90 to the position shown in FIG. 2 , when actuating pressure is vented from cylinder 140 .
- the front support 24 is formed with passages, preferably spaced mutually about axis 11 . These passages in front support 24 are represented in the FIGS. 1 and 2 by passage lengths 150 , 151 , 152 , through which hydraulic fluid is supplied to clutch servo cylinders 114 , 116 , brake servo cylinder 140 , and balance dams 120 , 122 .
- a passage of each of the front support passages communicates hydraulic fluid and pressure to cylinders 114 , 116 and balance dams 120 , 122 of the front cylinder assembly 36 through the fluid passages 109 , 110 , 111 , 112 , 113 , 124 formed in the front cylinder assembly 36 .
- Another passage of each of the front support passages communicates hydraulic fluid and pressure to cylinder 140 of the middle cylinder assembly 86 through the fluid passages 142 , 143 in carrier 32 .
- the front support 24 includes a bearing support shoulder 154 , which extends axially and over an axial extension 156 of the front cylinder assembly 36 .
- a bushing 158 and bearing 160 provide for rotation of the front cylinder assembly 36 relative to the front support 24 .
- This arrangement of the front support 24 , its bearing support shoulder 154 , and front cylinder assembly 36 prevents radial access required to machine a passage or passages that would connect first passage 152 in front support 24 to the second passage 109 in the front cylinder assembly 36 .
- first passage 152 is formed with an opening that extends along a length of first passage 152 , parallel to axis 11 , and through an outer wall of the front support 24 .
- the opening faces radially outward toward second passage 109 .
- second passage 109 is formed with a second opening that extends along a length of second passage 109 , parallel to axis 11 , and through an inner wall of the front cylinder assembly 36 .
- the second opening faces radially inward toward first passage 152 .
- a first sleeve 162 is inserted axially with a press fit over a surface at an outer diameter of the front support 24 , thereby covering the opening at the outer surface of passage length 152 .
- Sleeve 162 is formed with radial passages 164 , 165 , which extend through the thickness of the sleeve 162 .
- Seals 176 located at each side of the passages 164 , 165 prevent leakage of fluid from the passages.
- a second sleeve 170 is inserted axially with a press fit over the second opening at the inside diameter of the front cylinder assembly 36 , thereby covering and enclosing the length of the second opening in the second passage 109 .
- Sleeve 170 is formed with radial openings, two of which are represented in FIG. 2 by openings 172 , 174 , aligned with the radial passages 164 , 165 formed in the first sleeve 162 .
- Sleeves 164 and 170 provides hydraulic continuity from the source of fluid pressure carried in the passages of the front support 24 to the balance dams 120 , 122 and the servo cylinders 114 , 116 , 140 , through which clutches 76 , 80 and brake 88 are actuated.
- Sleeves 162 , 170 also provide access that enables machining of the first and second passages 152 , 109 in the surface at the outside diameter of front support 24 and in the surface at the inside diameter of the front cylinder assembly 36 .
- FIG. 3 shows sleeves 162 , 170 and three seals 176 , which are fitted in recesses on sleeve 162 between each of its radial passages 164 , 165 .
- FIG. 4 shows output pinion 70 meshes with a transfer gear 180 , which is formed integrally with transfer pinion 182 on a transfer wheel 184 .
- a transfer shaft 186 is secured at one end by a pinned connection 188 to a non-rotating housing component 190 , and at the opposite end is seated in a recess 192 formed in a non-rotating torque converter housing component 194 .
- Ball bearing 198 supports transfer wheel 184 on the torque converter housing 194 .
- Housing components 190 , 194 comprise a reaction component and may be formed integrally or preferably as separate components.
- Ball bearing 198 is supported radially by being seated on a surface 196 of the torque converter housing 194 .
- a shoulder 199 on torque converter housing 194 contacts the right-hand axial surface of the inner race of bearing 198 , the second surface of bearing 198 .
- a snap ring 200 contacts the right-hand axial third surface 201 of the outer race of bearing 198 . Shoulder 199 and snap ring 200 limit rightward axial movement of bearing 198 .
- the thrust washer 204 contacts a shoulder 206 formed on transfer shaft 186 . Shoulders 202 and 206 limit leftward axial movement of bearing 198
- the ring gear 210 of a differential mechanism 212 meshes with transfer pinion 182 and is supported for rotation by bearings 214 , 216 on housing 190 , 194 .
- Rotating power transmitted to output pinion 70 is transmitted through transfer gears 180 , 182 and ring gear 210 to the input of differential, which drives a set of vehicle wheels aligned with axis 220 .
- a roller bearing 222 supports transfer wheel 184 on transfer shaft 186 .
- the thickness of a washer 224 is selected to ensure contact between thrust washer 204 and the inner race of bearing 198 .
- the output pinion 70 and transfer gears 180 , 182 have helical gear teeth, which produce thrust force components in the axial direction parallel to axis 220 and in the radial direction, normal to the plane of FIG. 4 .
- a thrust force in the right-hand direction transmitted to the transfer gear wheel 184 is reacted by the torque converter housing 194 due to its contact at shoulder 199 with bearing 198 .
- a thrust force in the left-hand direction transmitted to the transfer gear wheel 184 is reacted by the housing 190 due to contact between snap ring 200 and bearing 198 , contact between bearing 198 and thrust washer 204 , contact between the thrust washer and transfer shaft 186 , and contact between shaft 186 , washer 224 and housing 190 .
- the D brake 104 includes a first set of thin discs 230 secured to the outer race 232 of one-way brake 106 by a spline connection, which permits the discs 230 to move axially and prevents them from rotating relative to the race 232 , which is fixed to the transmission case or end cover against rotation.
- the D brake 104 includes a second set of thin discs 234 secured to the inner race 107 of one-way brake 106 by a spline connection, which permits the discs 234 to move axially and prevents them from rotating relative to the inner race 107 .
- Inner race 107 is fixed to the carrier 68 of gearset 46 , such that they rotate together as a unit at the same speed.
- the outer and inner races 232 , 107 of one-way brake 106 are formed of a ferrous alloy of sintered powdered metal, and discs 230 , 234 are of steel.
- the one-way brake 106 is a rocker one-way brake of the type having a pivoting rockers, each rocker retained is a pocket and actuated by centrifugal force and a compression spring, as described in U.S. Pat. Nos. 7,448,481 and 7,451,862.
- the reaction spline for the D clutch 104 is preferably not formed in the aluminum case or end cover because of high local stresses caused by the thin discs 232 , 234 used to reduce parasitic loss.
- the D clutch reaction splines are formed as an integral part of the raceways of the one-way brake 106 . The brake 106 is then splined to the transmission case.
- the final drive mechanism of FIG. 5 produces a drive connection between the output pinion 70 and the input of the differential mechanism 212 .
- Output pinion 70 meshes with output gear 270 , which is supported on a ball bearing 272 and roller bearings 274 , 275 .
- Bearing 272 is supported on the transmission case 26 ; bearings 274 , 275 are supported on an extension 276 , which is bolted to the case.
- a planetary final drive gearset 278 includes a sun gear 280 , secured to the output gear 270 ; a ring gear 282 , secured to the input of differential 212 ; a carrier 285 , fixed against rotation by a spline connection 284 to the cover extension 276 ; and planet pinions 287 supported on the carrier 285 and meshing with the sun gear 280 and ring gear 282 .
- the final drive gearset 278 drives the differential input at a speed that is reduced relative to the speed of output gear 270 and reverses the direction of rotation relative to the direction of rotation of output gear 270 .
- the differential drives the axle shafts, which are secured to the driven wheels.
- the final drive mechanism of FIG. 5 produces a drive connection between the output pinion 70 and the input of the differential mechanism 212 .
- Output pinion 70 meshes with output gear 270 , which is supported on a ball bearing 272 and roller bearings 274 , 275 .
- Bearing 272 is supported on the transmission case 26 ; bearings 274 , 275 are supported on an extension 276 , which is bolted to the case.
- a planetary final drive gearset 278 includes a sun gear 280 , secured to the output gear 270 ; a ring gear 282 , secured to the input of differential 212 ; a carrier 285 , fixed against rotation by a spline connection 284 to the cover extension 276 ; and planet pinions 287 supported on the carrier 285 and meshing with the sun gear 280 and ring gear 282 .
- the final drive gearset 278 drives the differential input at a speed that is reduced relative to the speed of output gear 270 and reverses the direction of rotation relative to the direction of rotation of output gear 270 .
- the differential drives the axle shafts, which are secured to the driven wheels.
- the drive mechanism shown in FIGS. 6 and 7 produces a drive connection between output pinion 70 and the input of a differential mechanism 300 , centered on axis 302 , through a final drive 304 , centered on axis 306 .
- the drive mechanism also produces a drive connection between output pinion 70 and a power-take-off (PTU) mechanism 308 , centered on axis 310 , through a gear 312 , centered on axis 314 .
- PTU power-take-off
- the final drive gear wheel 304 includes a gear 318 , which meshes with output pinion 70 , and a pinion 320 , which is formed integrally with gear 318 and meshes with the ring gear 322 of differential mechanism 300 .
- a shaft 324 journalled on front support 326 and transmission housing 26 , supports the gear wheel 304 .
- a roller bearing 328 and ball bearing 330 support gear wheel 304 on shaft 324 and front support 326 , respectively.
- the side bevel gears 332 , 334 of differential mechanism 300 are connected by splines to halfshafts 336 , 338 , which transmits rotating power to the front vehicle wheels.
- Bearings 340 , 342 at least partially support the halfshafts on front support 326 and housing 26 , respectively.
- FIG. 7 illustrates the vehicle's longitudinal axis 344 , and shows that the axis of the front wheels is located with respect to the vehicle's lateral axis, forward of the axis 11 , on which the engine's crankshaft and the transmission input shaft 20 are centered.
- Output pinion 70 also meshes with gear 318 , which meshes with a PTU gear 350 , supported by bearings 352 , 354 on front support 326 and transmission housing 26 , respectively.
- a clutch 356 is closed producing a drive connection between output pinion 70 and shaft 358 of power-take-off (PTU) mechanism 308 , which transmits power to the rear wheels of the vehicle. All-wheel drive operation is terminated when clutch 356 is open.
- PTU power-take-off
- FIG. 7 illustrates that the axis 310 of the power-take-off (PTU) mechanism 308 is located along the vehicle's longitudinal axis 344 , rearward of the axis 11 of the engine crankshaft and transmission input shaft 20 .
- PTU power-take-off
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Abstract
Description
- This application is a continuation-in-part of pending U.S. application Ser. No. 13/052,376, filed Mar. 21, 2011.
- 1. Field of the Invention
- This invention relates to an automatic transmission for a motor vehicle that includes planetary gearsets and clutches and brakes whose state of engagement and disengagement determines speed ratios produced by the transmission.
- 2. Description of the Prior Art
- In a front wheel drive vehicle, the axial space available for the transmission is limited by the width of the engine compartment and the length of the engine. In addition, the trend to increase the number of ratios available generally increases the number of components required. For these reasons, it is desirable to position components concentrically in order to minimize axial length. The ability to position components concentrically is limited, however, by the need to connect particular components mutually and to the transmission case.
- Furthermore, it is desirable for the output element to be located near the center of the vehicle, which corresponds to the input end of the gear box. An output element located toward the outside of the vehicle may require additional support structure and add length on the transfer axis. With some kinematic arrangements, however, the need to connect certain elements to the transmission case requires that the output element be so located.
- Chain drive transaxle final drive systems with grounded ring planetary gear sets have unacceptable noise, vibration and harshness properties due to chain lash. Transfer shaft gearing systems limit overall gear ratio.
- A drive mechanism includes a transmission including a pinion centered at an axis, a differential mechanism centered at a second axis forward of the axis, driveably connected to the pinion through a gear wheel meshing with the pinion, and a power take-off mechanism centered at a third axis rearward of the axis, driveably connected to the pinion, including a clutch that alternately opens and closes a drive connection to the pinion.
- The drive mechanism satisfies a vehicle styling requirement that locates the front wheel axles, with respect to the lateral axis of the vehicle, forward of the engine and provides all-wheel drive (AWD) operation. The power-take off (PTU) is integrated into the front wheel drive transaxle.
- The scope of applicability of the preferred embodiment will become apparent from the following detailed description, claims and drawings. It should be understood, that the description and specific examples, although indicating preferred embodiments of the invention, are given by way of illustration only. Various changes and modifications to the described embodiments and examples will become apparent to those skilled in the art.
- The invention will be more readily understood by reference to the following description, taken with the accompanying drawings, in which:
-
FIG. 1 is a cross sectional side view of a multiple speed automatic transaxle; -
FIG. 2 is cross sectional side view of the transaxle showing the front and middle cylinder assemblies; -
FIG. 3 is a side perspective view showing sleeves that are fitted on the front support and middle cylinder assembly, respectively; -
FIG. 4 is a view cross sectional side view of the transfer gears and shaft near the output of the transaxle; -
FIG. 5 is a cross sectional side view of a multiple speed automatic transaxle having an alternate final drive mechanism from that ofFIG. 4 ; -
FIG. 6 is a cross sectional side view of a multiple speed automatic transaxle showing a power take-off mechanism and an alternate final drive; and -
FIG. 7 is a schematic diagram showing the arrangement of the principal axes of the transmission, power take-off mechanism and final drive ofFIG. 6 . - Referring now to the drawings,
FIG. 1 illustrates gearing, clutches, brakes, shafts, fluid passages, and other components of a multiple-speed automatic transaxle 10 arranged substantially concentrically about anaxis 11. - A torque converter includes an impeller driven by an engine, a turbine hydrokinetically coupled to the impeller, and a stator between the impeller and turbine. A
transmission input shaft 20 is secured by aspline connection 21 to the turbine. The stator is secured by aspline connection 22 to afront support 24, which is secured against rotation to atransmission case 26. - A double pinion, speed reduction
planetary gearset 28 includes asun gear 30, secured by aspline connection 31 toinput shaft 20; acarrier 32, secured by aspline connection 33 to thefront support 24; aring gear 34, secured by a spline connection 35 to afront cylinder assembly 36; a first set ofplanet pinions 38 supported oncarrier 32 and meshing withsun gear 30; and a second set ofplanet pinions 40, supported oncarrier 32 and meshing withring gear 34 and thefirst pinions 38.Ring gear 34 rotates in the same direction asinput shaft 20 but at a reduced speed. -
Rear gearset 46 andmiddle gearset 48 are simple planetary gearsets. Gearset 46 includes a set ofplanet pinion 50 supported for rotation oncarrier 52 and meshing with bothsun gear 54 andring gear 56. Gearset 48 includes a set ofplanet pinions 58 supported for rotation oncarrier 60 and meshing with bothsun gear 62 andring gear 64. Sungear 54 is splined to a shaft that is splined to ashell 66, on whichshaft sun gear 62 is formed, thereby securing thesun gears shell 66. Carrier 52 is fixed to ashell 68.Carrier 60 andring gear 56 are fixed to each other and to outputpinion 70 through ashell 72.Ring gear 64 is fixed toshell 74. -
Front cylinder assembly 36, which is fixed toring gear 34, actuatesclutches clutch 76 includes plates splined tofront cylinder assembly 36 alternating with plates splined toshell 74. When hydraulic pressure is applied topiston 78, the plates are forced together and torque is transmitted betweenring gears ring gears clutch 80 include plates splined tofront cylinder assembly 36 alternating with plates splined toshell 66. When hydraulic pressure is applied topiston 82, torque is transmitted betweenring gear 34 andsun gears control body 84, throughfront support 24, intofront cylinder assembly 36 between rotating seals. -
Middle cylinder assembly 86, which includescarrier 32, actuatesbrake 88. Plates forbrake 88 include plates splined tocarrier 32 alternating with plates splined toshell 66. When hydraulic pressure is applied topiston 90, the brake holdssun gears control body 84, throughfront support 24, betweenplanet pinions middle cylinder assembly 86. Due to the location ofclutch pack 88,output element 70 is located in the more favorable position near the front of the gear box. -
Rear cylinder assembly 92 is secured by aspline connection 93 fixed toinput shaft 20. When hydraulic pressure is applied topiston 94, the plates ofclutch 96 transmit torque betweeninput shaft 20 andcarrier 52. Similarly, when hydraulic pressure is applied topiston 98, the plates ofclutch 100 transmit torque betweeninput shaft 20 andsun gears control body 84, intorear cylinder assembly 92. - When hydraulic pressure is applied to
piston 102,brake 104 holdscarrier 52 andshell 68 against rotation. A one-way brake 106 passively preventscarrier 52 and shell 68 from rotating in the negative direction, but allows them to rotate in the forward direction. One-way brake 106 may optionally be omitted and its function performed by actively controllingbrake 104. - The
D brake 104 is used only as a latching device not as a dynamic brake. To minimize parasitic viscous drag loss produced inbrake 104 it is desired that excess oil not be present in the brake. Therefore, an oil dam formed by anoil seal 103 between thepiston 94 of E clutch 96 and theinner race 107 of one-way brake 106 is provided to limit or prevent oil from entering theD brake 104. The inner radial end ofreturn spring 108 continually contacts thepiston 102 that actuatesbrake 104. The outer radial end ofreturn spring 108 continually contacts a fixed structure, so that the spring flexes as thepiston 102 moves in the cylinder of theD brake 104. In this way,return spring 108 also participates in the oil dam by limiting or preventing radial flow of oil into theD brake 104 caused by centrifugal force. - This arrangement permits
brake 88 andclutches planetary gearsets clutches planetary gearing Clutches brakes - As
FIGS. 2A , 2B illustrate, thefront cylinder assembly 36 is supported for rotation on the fixedfront support 24 andcarrier 34. Thefront cylinder assembly 36 is formed with clutch actuation fluid passages, each passage communicating with one of thecylinders front cylinder assembly 36.Cylinder 114 containspiston 78;cylinder 116 containspiston 82. One of the fluid passages infront cylinder assembly 36 is represented inFIG. 2 byinterconnected passage lengths cylinder 116 communicates with a source of clutch control hydraulic pressure. Another of the fluid passages infront cylinder assembly 36, which is similar topassage lengths axis 11 frompassage lengths cylinder 114.Passage lengths 109 are machined in the surface at the inside diameter of thefront cylinder assembly 36. - The
front cylinder assembly 36 is also formed with a balance volume supply passage, similar to, but spaced angularly aboutaxis 11 frompassage lengths balance volumes FIG. 2A , the balance volume supply passage includes anaxial passage length 124, which communicates with a source of balance volume supply fluid and pressure, and aradial passage length 126, through which fluid flows into thebalance volumes passage 124.Passage 124 may be a single drilled hole extending along a longitudinal axis and located between the two clutch balance areas of the A clutch and B clutch.Passage 124 carries fluid to cross drilledholes 126, which communicate with thebalance volumes - Coiled compression springs 128, 130, each located in a
respective balance dam respective piston FIG. 2 .Ring gear 34 is secured tofront cylinder assembly 36 by aspline connection 132. -
Middle cylinder assembly 86 includescarrier 32, which is grounded on thefront support 24.Carrier 32 includes first andsecond plates shaft supporting pinions 38, and the other pinionshaft supporting pinions 40.Plate 135 is formed with acylinder 140 containing abrake piston 90. - A source of brake actuating hydraulic pressure communicates with
cylinder 140 through a series oninterconnected passage lengths passage 143, through a web ofcarrier 32, between the sets of planet pinions 38, 40, tocylinder 140. These brake feed passages are formed incarrier 32. When actuating pressure is applied tocylinder 140,piston 90 forces the plates ofbrake 88 into mutual frictional contact, thereby holding sun gears 54, 62 andshell 66 against rotation. ABelleville spring 146 returnspiston 90 to the position shown inFIG. 2 , when actuating pressure is vented fromcylinder 140. - The
front support 24 is formed with passages, preferably spaced mutually aboutaxis 11. These passages infront support 24 are represented in theFIGS. 1 and 2 bypassage lengths clutch servo cylinders brake servo cylinder 140, andbalance dams cylinders balance dams front cylinder assembly 36 through thefluid passages front cylinder assembly 36. Another passage of each of the front support passages communicates hydraulic fluid and pressure tocylinder 140 of themiddle cylinder assembly 86 through thefluid passages carrier 32. - The
front support 24 includes abearing support shoulder 154, which extends axially and over anaxial extension 156 of thefront cylinder assembly 36. Abushing 158 and bearing 160 provide for rotation of thefront cylinder assembly 36 relative to thefront support 24. This arrangement of thefront support 24, itsbearing support shoulder 154, andfront cylinder assembly 36, however, prevents radial access required to machine a passage or passages that would connectfirst passage 152 infront support 24 to thesecond passage 109 in thefront cylinder assembly 36. - To overcome this problem and provide hydraulic continuity between
passage lengths first passage 152 is formed with an opening that extends along a length offirst passage 152, parallel toaxis 11, and through an outer wall of thefront support 24. The opening faces radially outward towardsecond passage 109. Similarly,second passage 109 is formed with a second opening that extends along a length ofsecond passage 109, parallel toaxis 11, and through an inner wall of thefront cylinder assembly 36. The second opening faces radially inward towardfirst passage 152. - A
first sleeve 162 is inserted axially with a press fit over a surface at an outer diameter of thefront support 24, thereby covering the opening at the outer surface ofpassage length 152.Sleeve 162 is formed withradial passages sleeve 162.Seals 176, located at each side of thepassages - A
second sleeve 170 is inserted axially with a press fit over the second opening at the inside diameter of thefront cylinder assembly 36, thereby covering and enclosing the length of the second opening in thesecond passage 109.Sleeve 170 is formed with radial openings, two of which are represented inFIG. 2 byopenings 172, 174, aligned with theradial passages first sleeve 162. -
Sleeves front support 24 to thebalance dams servo cylinders clutches brake 88 are actuated. -
Sleeves second passages front support 24 and in the surface at the inside diameter of thefront cylinder assembly 36.FIG. 3 showssleeves seals 176, which are fitted in recesses onsleeve 162 between each of itsradial passages - As
FIG. 4 showsoutput pinion 70 meshes with atransfer gear 180, which is formed integrally withtransfer pinion 182 on atransfer wheel 184. Atransfer shaft 186, is secured at one end by a pinnedconnection 188 to anon-rotating housing component 190, and at the opposite end is seated in arecess 192 formed in a non-rotating torqueconverter housing component 194.Ball bearing 198 supportstransfer wheel 184 on thetorque converter housing 194.Housing components -
Ball bearing 198 is supported radially by being seated on asurface 196 of thetorque converter housing 194. Ashoulder 199 ontorque converter housing 194 contacts the right-hand axial surface of the inner race of bearing 198, the second surface ofbearing 198. Asnap ring 200 contacts the right-hand axialthird surface 201 of the outer race ofbearing 198.Shoulder 199 andsnap ring 200 limit rightward axial movement ofbearing 198. - A
shoulder 202 formed ongear wheel 184 contacts the left-hand axial first surface of the outer race ofbearing 198. Athrust washer 204 contacts a left-hand axialfourth surface 205 of the inner race ofbearing 198. Thethrust washer 204 contacts ashoulder 206 formed ontransfer shaft 186.Shoulders bearing 198 - The
ring gear 210 of adifferential mechanism 212 meshes withtransfer pinion 182 and is supported for rotation bybearings housing - Rotating power transmitted to
output pinion 70 is transmitted through transfer gears 180, 182 andring gear 210 to the input of differential, which drives a set of vehicle wheels aligned withaxis 220. - A
roller bearing 222 supportstransfer wheel 184 ontransfer shaft 186. The thickness of awasher 224, fitted in arecess 226 ofhousing 190, is selected to ensure contact betweenthrust washer 204 and the inner race ofbearing 198. - The
output pinion 70 and transfer gears 180, 182 have helical gear teeth, which produce thrust force components in the axial direction parallel toaxis 220 and in the radial direction, normal to the plane ofFIG. 4 . A thrust force in the right-hand direction transmitted to thetransfer gear wheel 184 is reacted by thetorque converter housing 194 due to its contact atshoulder 199 withbearing 198. A thrust force in the left-hand direction transmitted to thetransfer gear wheel 184 is reacted by thehousing 190 due to contact betweensnap ring 200 andbearing 198, contact betweenbearing 198 and thrustwasher 204, contact between the thrust washer andtransfer shaft 186, and contact betweenshaft 186,washer 224 andhousing 190. - As shown in
FIG. 1A , theD brake 104 includes a first set ofthin discs 230 secured to theouter race 232 of one-way brake 106 by a spline connection, which permits thediscs 230 to move axially and prevents them from rotating relative to therace 232, which is fixed to the transmission case or end cover against rotation. - Similarly, the
D brake 104 includes a second set ofthin discs 234 secured to theinner race 107 of one-way brake 106 by a spline connection, which permits thediscs 234 to move axially and prevents them from rotating relative to theinner race 107.Inner race 107 is fixed to thecarrier 68 ofgearset 46, such that they rotate together as a unit at the same speed. Preferably the outer andinner races way brake 106 are formed of a ferrous alloy of sintered powdered metal, anddiscs way brake 106 is a rocker one-way brake of the type having a pivoting rockers, each rocker retained is a pocket and actuated by centrifugal force and a compression spring, as described in U.S. Pat. Nos. 7,448,481 and 7,451,862. - The reaction spline for the D clutch 104 is preferably not formed in the aluminum case or end cover because of high local stresses caused by the
thin discs way brake 106. Thebrake 106 is then splined to the transmission case. - The final drive mechanism of
FIG. 5 produces a drive connection between theoutput pinion 70 and the input of thedifferential mechanism 212.Output pinion 70 meshes withoutput gear 270, which is supported on aball bearing 272 androller bearings transmission case 26;bearings extension 276, which is bolted to the case. - A planetary
final drive gearset 278 includes asun gear 280, secured to theoutput gear 270; aring gear 282, secured to the input ofdifferential 212; acarrier 285, fixed against rotation by aspline connection 284 to thecover extension 276; and planet pinions 287 supported on thecarrier 285 and meshing with thesun gear 280 andring gear 282. Thefinal drive gearset 278 drives the differential input at a speed that is reduced relative to the speed ofoutput gear 270 and reverses the direction of rotation relative to the direction of rotation ofoutput gear 270. The differential drives the axle shafts, which are secured to the driven wheels. - The final drive mechanism of
FIG. 5 produces a drive connection between theoutput pinion 70 and the input of thedifferential mechanism 212.Output pinion 70 meshes withoutput gear 270, which is supported on aball bearing 272 androller bearings transmission case 26;bearings extension 276, which is bolted to the case. - A planetary
final drive gearset 278 includes asun gear 280, secured to theoutput gear 270; aring gear 282, secured to the input ofdifferential 212; acarrier 285, fixed against rotation by aspline connection 284 to thecover extension 276; and planet pinions 287 supported on thecarrier 285 and meshing with thesun gear 280 andring gear 282. Thefinal drive gearset 278 drives the differential input at a speed that is reduced relative to the speed ofoutput gear 270 and reverses the direction of rotation relative to the direction of rotation ofoutput gear 270. The differential drives the axle shafts, which are secured to the driven wheels. - The drive mechanism shown in
FIGS. 6 and 7 produces a drive connection betweenoutput pinion 70 and the input of adifferential mechanism 300, centered onaxis 302, through afinal drive 304, centered onaxis 306. The drive mechanism also produces a drive connection betweenoutput pinion 70 and a power-take-off (PTU)mechanism 308, centered onaxis 310, through agear 312, centered onaxis 314. - The final
drive gear wheel 304 includes agear 318, which meshes withoutput pinion 70, and apinion 320, which is formed integrally withgear 318 and meshes with thering gear 322 ofdifferential mechanism 300. Ashaft 324, journalled onfront support 326 andtransmission housing 26, supports thegear wheel 304. Aroller bearing 328 andball bearing 330support gear wheel 304 onshaft 324 andfront support 326, respectively. Theside bevel gears differential mechanism 300 are connected by splines to halfshafts 336, 338, which transmits rotating power to the front vehicle wheels. Bearings 340, 342 at least partially support the halfshafts onfront support 326 andhousing 26, respectively. -
FIG. 7 illustrates the vehicle'slongitudinal axis 344, and shows that the axis of the front wheels is located with respect to the vehicle's lateral axis, forward of theaxis 11, on which the engine's crankshaft and thetransmission input shaft 20 are centered. -
Output pinion 70 also meshes withgear 318, which meshes with aPTU gear 350, supported bybearings front support 326 andtransmission housing 26, respectively. When all-wheel drive operation is desired, a clutch 356 is closed producing a drive connection betweenoutput pinion 70 andshaft 358 of power-take-off (PTU)mechanism 308, which transmits power to the rear wheels of the vehicle. All-wheel drive operation is terminated when clutch 356 is open. -
FIG. 7 illustrates that theaxis 310 of the power-take-off (PTU)mechanism 308 is located along the vehicle'slongitudinal axis 344, rearward of theaxis 11 of the engine crankshaft andtransmission input shaft 20. - In accordance with the provisions of the patent statutes, the preferred embodiment has been described. However, it should be noted that the alternate embodiments can be practiced otherwise than as specifically illustrated and described.
Claims (18)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/552,717 US8939862B2 (en) | 2011-03-21 | 2012-07-19 | Final drive mechanism and power take off for a transmission |
DE201310107513 DE102013107513A1 (en) | 2012-07-19 | 2013-07-16 | Axle drive mechanism and power take-off for a transmission |
CN201310299477.XA CN103573977B (en) | 2012-07-19 | 2013-07-17 | Final drive mechanism and power take off for a transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/052,376 US8403798B2 (en) | 2011-02-24 | 2011-03-21 | Final drive mechanism for a transmission |
US13/552,717 US8939862B2 (en) | 2011-03-21 | 2012-07-19 | Final drive mechanism and power take off for a transmission |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US13/052,376 Continuation-In-Part US8403798B2 (en) | 2011-02-24 | 2011-03-21 | Final drive mechanism for a transmission |
Publications (2)
Publication Number | Publication Date |
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US20120279327A1 true US20120279327A1 (en) | 2012-11-08 |
US8939862B2 US8939862B2 (en) | 2015-01-27 |
Family
ID=47089324
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US13/552,717 Expired - Fee Related US8939862B2 (en) | 2011-03-21 | 2012-07-19 | Final drive mechanism and power take off for a transmission |
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US (1) | US8939862B2 (en) |
CN (1) | CN103573977B (en) |
DE (1) | DE102013107513A1 (en) |
Cited By (5)
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US20140113762A1 (en) * | 2012-10-23 | 2014-04-24 | Ford Global Technologies, Llc | Automatic transmission assembly |
CN104235280A (en) * | 2013-06-21 | 2014-12-24 | 福特全球技术公司 | Transmission with integrated clutch and gear set |
US9573463B2 (en) | 2013-05-17 | 2017-02-21 | Ford Global Technologies, Llc | Transmission having selectable power transfer shaft |
WO2018103777A1 (en) * | 2016-12-07 | 2018-06-14 | Schaeffler Technologies AG & Co. KG | Clutch and brake system having a braking device nested with an actuating system; and drive train |
WO2018103778A1 (en) * | 2016-12-07 | 2018-06-14 | Schaeffler Technologies AG & Co. KG | Clutch and brake system having a friction element carrier receiving a friction element and a brake element; and drive train |
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JP6064965B2 (en) * | 2014-10-08 | 2017-01-25 | トヨタ自動車株式会社 | Four-wheel drive device for vehicle |
US9523396B2 (en) * | 2014-12-08 | 2016-12-20 | Gm Global Technology Operations, Llc | Hydraulic dog clutch |
US10400883B2 (en) | 2017-01-04 | 2019-09-03 | United Technologies Corporation | Gear with fluid control dam and apertures |
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Also Published As
Publication number | Publication date |
---|---|
CN103573977B (en) | 2017-05-10 |
DE102013107513A1 (en) | 2014-01-23 |
CN103573977A (en) | 2014-02-12 |
US8939862B2 (en) | 2015-01-27 |
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